Vane assembly in rotary fluid machines



Nov. 24, 1964 K. EICKMANN 3,158,103

VANE; ASSEMBLY IN ROTARY FLUID MACHINES Original Filed Feb. 9, 1959 5 Sheets-Sheet 1 2 3 FIG. 1

IFIGB INVENTOR KARL EICKMANN K diat ww ATTORNEYS Nov. 24, 1964 K. EICKMANN 3,158,103

VANE ASSEMBLY IN ROTARY FLUID MACHINES Original Filed Feb. 9, 1959 5 Sheets-Sheet 2 w Z3 m m W S m//R\ Q a a a G. ////,m Ga 6. mm W H m P H F m IFIGZZ [FIGIG [FIGIZ ATTORNEYS Nov. 24, 1964 K. EICKMANN 3,158,103

VANE ASSEMBLY IN ROTARY FLUID MACHINES Original Filed Feb. 9, 1959 5 Sheets-Sheet 3 [Fl G. 25 IF I G. 24

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INVENTOR KARL EICKMANN BY y W 1 M ATTORNEYS Nov. 24, 1964 K. EICKMANN 3,158,103

VANE ASSEMBLY IN ROTARY FLUID MACHINES Qriginal Filed Feb. 9, 1959 5 Sheets-Sheet 4 INVENTOR KARL EICKMANN ATTORNEYS Nov. 24, 1964 K. EICKMANN 3,158,103

VANE ASSEMBLY IN ROTARY FLUID MACHINES Original Filed Feb. 9, 1959 5 Sheets-Sheet 5 [F I G 5| I INVENTOR 77 KARL E'ICKMANN ATTORNEYS United States Patent 3,158,103 VANE ASSEMBLY IN RGTARY FLUID MACHENES Karl Eiclrmann, Talmuchie, Kreis Calw, Germany (2420 Isshiki, Hayama-Machi, Kanagawa-Ken, depart) Griginai appiication Feb. 9, 1959, Ser. No. 792,031, new Patent No. 3,099,964, dated Aug. 6, 1963. Divided and this appiication lv lar. 2, 1.962, Ser. No. 176,945

Claims priority, application .Iapan Mar. 13, 1958 6 Claims. (Ql. 103136) This invention relates to a vane assembly in rotary fiuid machines, and more particularly to high pressure rotary vane machines which are provided with slots in the extension or side walls of the rotor. Vanes with axial and radial extensions are inserted into and carried by said slots and sliding elements are provided which contact the surface of the casing ring which surrounds the rotor. The sliding elements fit into the vanes extensions which embrace in a radial direction the casing ring provided between the side walls of the rotor, and are arranged in such a way that they may swing according to the movement of the vane towards the eccentric casing ring or the casing box in order to effect a tight seal.

This application is a division of my co-pending application Serial No. 792,001 filed Feb. 9, 1959, now Patent No. 3,099,964.

A typical rotary fluid machine is set forth in British Patent No. 744,446 (Feb. 8, 1956) in which a rotary fluid-driven engine, either a motor or pump, is provided with vanes which slide in slots located in the rotor and are enclosed by a casing ring, thereby defining compression cells. Each cell during rotation of the machine as a motor admits a fluid or pressure medium under pressure as the cell increases in volume and releases the fluid or medium as the cell decreases in volume, while in acting as a pump, the cell draws in the fluid or pressure medium by suction as the cell increases in volume and expels the fluid or'medium under pressure as the cell decreases in volume.

Though these vanes have been able to withstand a high pressure ten times higher than vanes which are'not provided in the side Walls of the rotor and furthermore might have been furnished with sliding elements fitting the casing ring, the sealing against leakage in the corners between the sliding elements and the extensions of the vane and the inner surface of the casing ring has been ineffective due to the fact that there was only point contact. Furthermore, by swinging the sliders, small openings appear between the casing ring, the axial ends of the slider and the vane extensions. These small openings cause leakage which may be negligible at low pres sure, but detrimental at rising eccentricity and at pressures of hundreds or" atmospheres. Vanes as known heretofore have also been provided with sliders smaller than the thickness of the vanes thereby permitting restricted radial pressure from the inside only. However, the slider and casing ring would wear thereby reducing pressure capacity.

Further, it has been attempted in the past to reduce friction between sliders or vanes and casing by lubricating grooves.

All these and similar constructions do not satisfy the requirements of modern machinery with regard to high efliciency and large power output.

These disadvantages have been overcome by the present invention which in detail provides:

(1) Effective sealing against leakage of fluids or gases due to closely fitting surface contact between the axial end-surfaces of the sliders and the vanes radial extensions embracing the former;

3,158,103 Patented Nov. 24, 1964 (2) Recesses on the radial outward portion of the sliders suitable to contain or receive fluids or gases under pressure which might increase forces directed radially to the axis of the rotor, while at the same time reducing the forces working radially outwards;

thus permitting higher speed and pressure between the sliders and casing ring and between the vanes and casing ring.

The present sealing eliect of such a vane assembly amounts to, in the case of hydraulic-oil in the working cells, an average leakage for the sum of the applied vanes and sliders (slide elements) of less than 0.8% ofthe units discharge at kg/cm. and in most cases, smaller than 3% at 300 l g./cm. pressure difierence between the chambers to be sealed.

The new vane assembly is suitable on engines and motors up to 10,000 I-LP. per one unit.

The invention is illustrated by the accompanying'drawingsinwhich: g

FIG. 1 is a partial sectional View of a rotary vane machine taken along the line 1--1 of FIG. 2 and along the line 11 of FIG. 3. FIG. 2 is a partial sectional view taken along the'line 22 of FIG. 1..

FIG. 3 is a partial sectional view taken along the lin 3-3 of FIG. 1.

FIG. 4 shows an embodiment of the vane slide element.

FIG. 5 is a sectional view taken along the line 5-5 of FIG. 6.

FIG. 6 is a top view of the vane slide element of FIG. 4.

IG. 7 shows an embodiment of the assembly of the vane and the vane slide element.

FIG. 8 is a sectional view taken along the line 8-8 of FIG. 7.

FIG. 9 is a top view of FIG. 7.

FIG. 10 is a further embodiment showing the vane slide element comprising two separate members.

FIG. 11 is a sectional view taken along the line 1111 of FIG. 10.

rotating-part of the vane'slide eleof FIG. 14.

FIG. 16 shows a further embodiment of the vane slide element comprising two separate members.

FIG. 17 is a sectional view taken along the line -1717 of FIG. 16.

FIG. 18 shows a rotating member of the vane slide element of :FIG. 16.

FIG. 19 is a sectional view taken along the line 1919 of FIG. 18. 1

FIG. 20 is a top view of the sliding member 16.

FIG. 21 is a sectional view taken along the line 21 21 of FIG. 20.

FIG. 22 is another embodiment of the vane having a slide element comprising two separatemembers.

FIG. 23 is a sectional view taken along the line 23- 23 of FIG. 22.

FIG. 24 is a side elevation view of the vane shown in FIG. 22, with the slide element removed.

FIG. 25 is a sectional view taken along the line 25-25 of FIG. 24.

FIG. 26 is a side view of the separate rotating member of the vane slide element of FIG. 22.

of FIG.

FIG. 27 is a sectional view taken along the line 27-27 of FIG. 26.

FIG. 28 is a side view of the separate sliding member of the vane slide element of FIG. 22.

FIG. 29 is a sectional view taken along the line 2929 of FIG. 28.

FIG. 30 is a side elevation view showing another embodiment similar to that of FIG. 22.

FIG. 31 is a sectional view taken along the line 31-31 of FIG. 30.

FIG. 32 is a side elevation view of the vane of FIG. 30 with the slide element removed.

FIG. 33 and FIG. 34 show sectional views taken along the lines 3333 and 34-34, respectively, of FIG. 32.

FIG. 35 and FIG. 36 show a side view and a sectional View, respectively, of the rotating member of the vane slide element of FIG. 30.

FIG. 37 and FIG. 38 show a side view and a sectional view, respectively, of the sliding member of the vane slide element of FIG. 30.

FIG. 39 is an embodiment of the vane in which the rotating member of the vane slide element is covered by a separate bearing cover.

FIG. 40 is a sectional view taken along the line 49-49 of FIG. 39.

FIG. 41 is a side elevation view of the vane shown in FIG. 39 with the slide element removed.

FIG. 42 and FIG. 43 show sectional views taken along lines 42-42 and 4343, respectively, of FIG. 41.

FIG. 44 shows a side elevation view of the bearing cover of the embodiment in FIG. 40.

FIG. 45 shows a sectional view taken along the line 45-45 of FIG. 44.

FIG. 46 and FIG. 47 are, respectively, a side view and a sectional view of a pin in FIG. 41.

FIG. 48 and FIG. 49 are, respectively, a side view and a sectional view of the rotating member of the vane slide element of the embodiment in FIG. 40.

FIG. 50 and FIG. 51 are, respectively, a side view and a sectional view of the sliding member of the vane slide element of the embodiment shown in FIG. 40.

FIG. 52 is a side view of the vane and slide element showing a further means for receiving the slide element in the vane.

FIG. 53 is a cross section along the line 53-53 of FIG. 52.

FIG. 54 is a side view of the vane shown in FIGS. 52 and 53 with the slide element removed.

FIG. 55 is a cross section along the line 5555 of FIG. 54.

Referring to the drawings, in FIGS. 1, 2 and 3, 1 represents a control shaft of a rotary piston machine, 2 is the rotor, and 3 represents bores guiding radially outwardly and inwardly the pressure medium to and from the slot space below the vane through the control shaft. 4 is a channel guiding outwardly the pressure medium from the rotor during each revolution of the machine. 5 is a shaft driving the rotor. 6 is a casing ring eccentric to the rotor. 7 and 8 are extended portions of the vane slot defined by the side walls of the rotor. 7a and 8a are pressure medium chambers located radially in the vane slot above the vane. 9 and 1d are side covers sealing axially and radially the side walls of the rotor. 11 are vanes of the rotary piston machine and 12 is a slide element thereon. 13 is an extended rotating member of the slide element adjacent the side wall. 14 is an extended portion of the vane located along the side wall and rotating therewith.

I5 and 16 are U-shaped portions located on the extended portions of the vane with projections to prevent the slide positioned therewithin from falling out of the vane. 17,

17a, 18 and 18a are balancing pressure recesses provided n the vane and which are covered in a separate divisional application, Serial No. 177,088, filed March 2, 1962, of the parent application.

As shown in FIGS. 1, 2 and 3, vanes 11 slide in radial guide slots 8 and 7 provided in rotor 2 and revolve together with the rotor. The rotary piston machine is enclosed by casing ring 6 and upon rotation vanes 11 are thrown radially outwardly by centrifugal and other forces, so that slide element 12, positioned on the top portion of the vane, abuts the inside surface of easing ring 6 and slides along the casing ring. In this way variable volume working cells or intervane spaces are formed between casing ring 6, vanes 11, slide elements 12, and the rotor and side walls with the side covers 9, 10 sealing the side walls axially and radially. During each revolution of the rotor, vanes 11 and slide elements 12 travel radially inwardly and outwardly, so that the capacity of Working cells is increased and decreased accordingly. Two adjacent working cells are shown in positions 30 and 39 in FIG. 3. These cells take up the working medium by means of distribution shatt 1 through the passages 29 during one half of the cycle and force the medium out through another passage or the distribution shafit 1 during the second half of the cycle. The rotor is driven by driving shaft 5, and the pressure medium leaves the rotor through bores 4. Passing through channels 3, the pressure medium enters slot chamber 28 radially below the vane through the distribution shaft. In these slot chambers, the pressure medium acts on the vane bottom forcing the vane radially outwardly. The vanes are shorter than the length of the slots located in the side walls or are provided with radial bores, grooves or slots, so that the pressure medium may flow radially outwardly along the lateral ends of the vanes.

In FIGS. 4, 5 and 6, 41 and 42 are rotating members of the slide element extended to fit adjacent the side wall of the rotor. 43 is the sliding surface of the sliding element adapted to slide along the casing ring. 44 is a balancing pressure recess provided in the slide element.

In FIGS. 7, 8 and 9, 45 is the vane and 48 and 49 are extended side portions of the vane which are fitted into the side walls of the rotor defining the slots and which are inwardly bent to prevent the slide element from falling out. 43 is the sliding member of the slide element and 44 is a balancing pressure recess. 41 and 42 are rotatable extended portions of the slide element in the extended parts of the vane.

FIGS. 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20 and 21 are views of rotating members of bipartite slide elements which permit the slides to rotate in the vanes. In these figures, 50, 51, 52 and 53 are the sliding members of various types of bipartite slide elements, to which the bolts 54, 55, 56 and 57 belong. The slide elements rotate with these sliding members passing along the casing ring. 58, S9, 60 and 61 are balancing pressure recesses provided in the slide elements. 62 and 63 are grooves in the sliding members for fitting therein the rotating members upon joining the two slide members together.

In FIGS. 22-29, 64 is a vane, 65 is a rotating member of the vane slide element and 66 is a sliding member of the slide element. 67 is a bore in the vane for supporting the rotating member of the slide element and 68 is a slot provided in the top face outwardly to the bore and radially to the vane. 69 is a bore provided in the sliding member of the vane slide element to fit therein the rotating member of the slide element.

In FIGS. 30-38, '74 is a vane, 71 is a rotating member of the slide element and 72 is a sliding member of the slide element. 73 is a bore provided in the vane to pivot the rotating member of the slide element, and 74 is a bore in the sliding member of the slide element for insertion of the rotating member.

In FIGS. 39-51, 75 is a vane, 76 is a rotating member of the vane slide element and 77 is a sliding member of the slide element. 78 is a bore provided in the vane to pivot the rotating member of the slide element. 79 is a groove provided above bore 78 along the extended vane portion radially to the vane for securing bearing cover 80.

slide element consisting of two separate members.

81 and 82 are small holes provided on the vane and the bearing cover for insertion of the pin'SS to connect vane 75 and bearing cover 80.

In FIGS. 52-55, 85 is a vane, and the slide element comprises a rotating member 86 and a sliding member 87. 88 is a slot provided at the side end extension of the vane for supporting the rotating member of the slide element.

The invention is more fully described by the following:

Constructions of embodiments of the slide element of the invention are illustrated in section in FIGS. 4, 5 and '6. The essential characteristic of the slide element in these embodiments is the revolving member which has the same radius as the channel on the top surface of the vane, so that the slide is pivotable around its axis in the channel. The sliding member of the slide element is constructed so that it abuts the side walls of the rotor and slides along the width of the casing ring; the wider sliding part of the slide being adapted to fit closely within a recess in the rotor. These balancing pressure fields created in the slide element recesses may result from many recesses or even from one recess.

FIGS. 7, 8 and 9 show a manner of fitting the slide element onto vane 45. Slide member 43 rotates with rotating members 41, 42 inserted into the vane. Edges 48, 49 of the vane are bent inwardly so that the slide may not become dislodged from the vane. The sliding member of the slide element is closely fitted between the extended side portions 48, 49 of the vane 45, sealing the space between sliding members 43 and side edges 43 and 49 of the vane.

FIGS. 10 and 11 show a constructional form of the Slidingmember 50 has a groove 61 into which rotating member 54 can be inserted and secured. FIGS. 12 and 13 show a form of the rotating member. FIGS. 14 and 15 indicate a form of the sliding member. The rotating member shown in FIGS. 10-15 has a particular advantage in that it can simply be constructed by grinding a cylindrical pin to form a halved member as shown in FIG. 13. Another advantage is that the rotating member, as a separate member, can be made so that its length is very accurate. In this way, it can be inserted snugly into the extended side part of the vane shown in FIG. 7, to elfect sealing and fitting by surface-contact between the sliders axial end surfaces and the vanes extended members. Furthermore, the construction of the slide element in two parts makes it possible to fit the rotating members into the vane, turn in edges 48, 49 (PEG. 8), and later secure the sliding member thereon separately.

The constructional form of the slide members shown in FIGS. l6, l7, 18, 19, and 21 has similar advantages to those of the two-piece slide element shown in FIGS. 10- 15. Thus, the rotating member is merely a shaft 56, 57 in ground cylindrical form, which is simply inserted into groove 62 of sliding member 53. 53 is a balancing pres- 1 sure recess.

The two-piece slide element shown in FIGS. 16-21, however, can only be employed where the vane and slide are forcibly directed between the casing ring and the guide rings, where rotating member 57 of the vane slide element is simply fitted into both grooves of the vane and slide member.

FIGS. 22-29, FIGS. 30-38 and FIGS. 39-51, respectively, show various improved embodiments according to the invention in which engagement between the sliding member and the rotating member of the vane slide and engagement between the rotating member and the vane itself permit advantageous employment of bipartite slide members as shown in FIG. 17. These embodiments are simple to manufacture and provide an improved sealing condition between adjacent vane cells.

In FIGS. 22-29, rotating member 65 of the vane slide is simply constructed as a cylindrical rod, more than half the face of which is enclosed by sliding member 66 of the vane slide upon assembly so that these members cannot be separated. Furthermore, rotating member 65 is pivoted within bore 67 in the extended portion of the vane which slides within the guide slot of the rotor side wall. Consequently, no leakage can occur between adjacent vane cells caused by lifting rotating member 65 from its channel along the top face of vane 64. The bore 67 of the vane is constructed ofa suitable diameter corresponding to that of rotating member 65. Slot 68-, disposed between the outer radial end faces of the extended portion of the vane, permits rotating member 65 of the vane slide to be slid into bore 67 where it is received under tension.

FIGS. 30-3 8, respectively, show an embodiment similar to those in FIGS. 22-29, but Without provision for a slot. In this embodiment, rotating member 71 of the vane slide is merely pushed and fitted into bore 73 of vane 70. Other features are similar to those of FIGS. 22-29.

In the embodiment shown in FIGS. 39 to 51, the halved bearing system, instead of the bore-bearing system, is employed. In this case, rotating member 76 of the vane slide is sustained in the semi-cylindrical shaped groove '78 of vane 75, and is covered by' bearing cover 80 from above. Bearing cover 80 is inserted into groove 79 provided at the top face of the extended portion of the vane and is secured to the vane by pin 83 which is inserted through pin holes 81, 32. Rotating member 76and sliding member 77 of the slide element are similar to those shown in FIGS. 22-29 and in FIGS. 30-38.

FIGS. 52-55 show an embodiment of a further means for receiving the vane slide. In this embodiment, a groove 88 is arranged at an angle of about 30 to 45 degrees with respect to the side of the vane, at the extended portion of vane 85. The slide element, consisting of rotating member 86 and the sliding member 87, is inserted into the groove 88 and rotatably supported via both ends of rotating member 86. In its location, within the guide slot of the rotor, the extended portions of the vane are positioned adjacent the side wall of the rotor, and the openings of slot 88 are sealed by the side walls so that the slide element cannot become dislodged during operation.

It is also possible to exchange the single elements of the various embodiments of the invention against each other. Especially, slide elements 50, 51, 53, 66, 72, 77, 87 or-43, having no recesses 44, 59, 60 or 61 on their slide surfaces, may be inserted-into the vane bodies 64, 70,

slide elements in relation to the casing ring'or the housing of the vane machine, recesses 44, 59, 60 or 61 have to be provided for fluids or gases under pressure. Conduits 68, 83 may be provided to connect recesses 44, 59, 60 or 61 with channels, chambers or other space containing fluid or gases under pressure. It is suitable to enlarge said recesses 44, 59, 60 or 61 to such an extent that the forces acting under pressure of fluids or gases in these recesses balance all or most of the other radial forces acting in opposition on the vane or on the slide element of the vane. In case of total balancing, the radial or almost radial forces of the fluids or gases under pressure are balanced completely so that the vanes with their slide elements are floating between the radial fluid or gas forces during their travel in the rotor. This fact saves friction and affords highest pressure and power output. The sealing effect of the present vane slider elements is effective up to several hundred atmospheres; The vane assembly according to the invention has been actually tested successfully at pressure peaks of about 10,000 p.s.i.

The invention applies to small vane machines of small horsepower as well as to those of several times higher than 10,000 horsepower, for example, for use in propeller drives for ships.

It will be obvious to those skilled in the art that while the application and drawings have been set forth herein to illustrate the invention, various changes and modifications 7? may be made without departing from the spirit and scope of the invention, which is to be limited only by the appended claims.

What is claimed is:

1. A rotary vane type engine comprising a casing having an inner circumferential surface defining a working chamber for receiving and discharging fluids, a rotor in said working chamber having an axis eccentric with respect thereto and provided with radial slots, vanes substantially radially 'slidable in said rotor slots and forming with said rotor and with said working chamber, expanding and contracting intervane spaces in which said fluid is received, said rotor extending in said casing axially and radially outwardly beyond the axial ends of said working chamber and said rotor slots in said rotor extending axially and radially outwardly beyond the ends of said working chamher, said vanes having corresponding end portions extending axially and radially outwardly beyond said working chamber in the extensions of said rotor slots, the portion of each vane within said working chamber having a radially outer top face substantially normal to the vertical axis of the vane, the end portions of each vane extending radially outwardly beyond said top face and having transverse medial faces substantially normal to said top face and radially inwardly terminating at the axial ends of said top face, a bearing groove arcuate in cross-section extending longitudinally in said top face normal to said transverse medial faces, a corresponding arcuate bearing groove extension passing longitudinally through each end portion of the Vans, each said groove extension having at least a partial cylindrical bearing surface extending more than 180", a substantially cylindrical rocker rod having a'correspondingly dimensioned arcuate bottom bearing portion pivotally and snugly fitting in said groove with the ends of the rod pivotally and snugly fitting in said groove extensions, and a slide element disposed on said rod and extending axially to the ends of the working chamber, said slide element having a radially outer face and a radially inner face, said radially inner face having a partial cylindrical groove delrned longitudinally therein extending circumferentially more than 180 and correspondingly dimensioned with respect to the radius of said rod to enclose pivotally and snugly the portion of said rod within said working chamber for permitting limited pivotal movement between said slide element and said rod and between said rod and said groove and groove extensions, the radially outer face of said slide element being slidably disposed against and in sealing contact with the casing inner surface, and the axial ends of said slide element having transverse end faces normal to the vane top face and parallel to the adjacent transverse medial faces of said vane end portions and extending radially in sealing pivotal abutment with said transverse medial faces, respectively.

2. Engine according to claim 1 wherein the casing inner surface and the rotor are displaceably mounted with respect to one another to permit adjustment of the eccentricity of the axes thereof, said casing inner surface being defined by a casing ring of at least partial cylindrical configuration surrounding said rotor und guiding said vanes.

3. Vane assembly, for a rotary vane type engine, which comprises a longitudinally extending vane having a top face and a bottom face, a vane lateral extension being provided at each longitudinal end of the vane,each vane lateral extension having a projection passing upwardly beyond the top face of said vane, said top face being provided with a longitudinally extending groove therein and each said projection being provided with a corresponding bore passage, a cylindrical rocker rod extending along said groove in said top face and being pivotally secured at its ends within said bore passages, and

a slide element disposed on said rocker rod and extend ing along said top face, the underside of said slide element having a partial cylindrical groove defined lon= gitudinally therein extending circumferentially more than 180 and correspondingly dimensional with respect to the radius of said rod to enclose pivotally and snugly the portion of said rod extending along said groove in said top face for permitting limited pivotal movement between said slide element and said rod.

4. In a vane assembly, for rotary fluid machines of the type having a casing with an inner circumferential surface defining a working chamber and a rotor with slots for carrying slidable vanes in slidable sealing contact with the casing inner surface to form intervene spaces in the working chamber, the improvement which cornprises a longitudinally extending vane having a central portion with a top face which is smaller in height with respect to the bottom face of the vane than the height of the two end portions of the vane, said end portions each having a transverse medial face adjacent said top face, sliding means pivotal between said end portions for cooperating with the inner circumferential surface of the casing to form a sliding seal, said slidin means having transverse end faces abutting the medial faces of said end portions and cooperating therewith to form a seal therebetween, the medial face of each said end portion extending upward-1y beyond the uppermost portion of the corresponding sliding means transverse end face, a groove defined longitudinally along said top face and a corresponding groove extension defined in each said end portion, sm'd groove and said groove extensions each having an arouate cross-section with substantially the same radius and axis of curvature, said groove extensions each having a pivotal hearing surface extending through an angle of curvature of more than 180, a substantially cylindrical rocker rod having substantially the same radius as said groove and groove extensions, said rod being disposed along said axis of curvature with its two ends pivotally and snugly fitting corresponding-1y within said bearing surfaces and its central portion pivotally and snugly fitting within said groove, the underside of said sliding means having a partial cylindrical groove defined longitudinally therein having an angle of curvature of more than 180 and substantially the same radius as said rod to enclose pivotally and snugly the portion of said rod extending along said groove for permitting limited pivotal movement not only between said rod and said groove and groove extensions but also between said rod and said sliding means.

5. Improvement according to claim 4 wherein said vane and sliding means are disposed in the corresponding slot therefor and forcibly directed radially outwardly against the inner surface of the casing.

6. Improvement according to claim 4 wherein said sliding means is provided with a balancing recess defined in the radially outer surface thereof to form with said casing inner surface a balance chamber for the reception of pressure fluid.

References Cited in the file of this patent UNlTED STATES PATENTS 1,658,524 Gurley Feb. 7, 1928 2,149,337 Deming Mar. 7, 1939 2,545,238 MacMi-l-lin Mar. 13, 1951 2,658,456 Wahlmark NOV. 10, 1953 2,755,741 Erskine July 24, 1956 FOREIGN PATENTS 9,499 Great Britain June 29, 1916 568,518 Great Britain Apr. 9, 1945 

1. A ROTARY VANE TYPE ENGINE COMPRISING A CASING HAVING AN INNER CIRCUMFERENTIAL SURFACE DEFINING A WORKING CHAMBER FOR RECEIVING AND DISCHARGING FLUIDS, A ROTOR IN SAID WORKING CHAMBER HAVING AN AXIS ECCENTRIC WITH RESPECT THERETO AND PROVIDED WITH RADIAL SLOTS, VANES SUBSTANTIALLY RADIALLY SLIDABLE IN SAID ROTOR SLOTS AND FORMING WITH SAID ROTOR AND WITH SAID WORKING CHAMBER, EXPANDING AND CONTRACTING INTERVANE SPACES IN WHICH SAID FLUID IS RECEIVED, SAID ROTOR EXTENDING IN SAID CASING AXIALLY AND RADIALLY OUTWARDLY BEYOND THE AXIAL ENDS OF SAID WORKING CHAMBER AND SAID ROTOR SLOTS IN SAID ROTOR EXTENDING AXIALLY AND RADIALLY OUTWARDLY BEYOND THE ENDS OF SAID WORKING CHAMBER, SAID VANES HAVING CORRESPONDING END PORTIONS EXTENDING AXIALLY AND RADIALLY OUTWARDLY BEYOND SAID WORKING CHAMBER IN THE EXTENSIONS OF SAID ROTOR SLOTS, THE PORTION OF EACH VANE WITHIN SAID WORKING CHAMBER HAVING A RADIALLY OUTER TOP FACE SUBSTANTIALLY NORMAL TO THE VERTICAL AXIS OF THE VANE, THE END PORTIONS OF EACH VANE EXTENDING RADIALLY OUTWARDLY BEYOND SAID TOP FACE AND HAVING TRANSVERSE MEDIAL FACES SUBSTANTIALLY NORMAL TO SAID TOP FACE AND RADIALLY INWARDLY TERMINATING AT THE AXIAL ENDS OF SAID TOP FACE, A BEARING GROOVE ARCUATE IN CROSS-SECTION EXTENDING LONGITUDINALLY IN SAID TOP FACE NORMAL TO SAID TRANSVERSE MEDIAL FACES, A CORRESPONDING ARCUATE BEARING GROOVE EXTENSION PASSING LONGITUDINALLY THROUGH EACH END PORTION OF THE VANE, EACH SAID GROOVE EXTENSION HAVING AT LEAST A PARTIAL CYLINDRICAL BEARING SURFACE EXTENDING MORE THAN 180*, A SUBSTANTIALLY CYLINDRICAL ROCKER ROD HAVING A CORRESPONDINGLY DIMENSIONED ARCUATE BOTTOM BEARING PORTION PIVOTALLY AND SNUGLY FITTING IN SAID GROOVE WITH THE ENDS OF THE ROD PIVOTALLY AND SNUGLY FITTING IN SAID GROOVE EXTENSIONS, AND A SLIDE ELEMENT DISPOSED ON SAID ROD AND EXTENDING AXIALLY TO THE ENDS OF THE WORKING CHAMBER, SAID SLIDE ELEMENT HAVING A RADIALLY OUTER FACE AND A RADIALLY INNER FACE, SAID RADIALLY INNER FACE HAVING A PARTIAL CYLINDRICAL GROOVE DEFINED LONGITUDINALLY THEREIN EXTENDING CIRCUMFERENTIALLY MORE THAN 180* AND CORRESPONDINGLY DIMENSIONED WITH RESPECT TO THE RADIUS OF SAID ROD TO ENCLOSE PIVOTALLY AND SNUGLY THE PORTION OF SAID ROD WITHIN SAID WORKING CHAMBER FOR PERMITTING LIMITED PIVOTAL MOVEMENT BETWEEN SAID SLIDE ELEMENT AND SAID ROD AND BETWEEN SAID ROD AND SAID GROOVE AND GROOVE EXTENSIONS, THE RADIALLY OUTER FACE OF SAID SLIDE ELEMENT BEING SLIDABLY DISPOSED AGAINST AND IN SEALING CONTACT WITH THE CASING INNER SURFACE, AND THE AXIAL ENDS OF SAID SLIDE ELEMENT HAVING TRANSVERSE END FACES NORMAL TO THE VANE TOP FACE AND PARALLEL TO THE ADJACENT TRANSVERSE MEDIAL FACES OF SAID VANE END PORTIONS AND EXTENDING RADIALLY IN SEALING PIVOTAL ABUTMENT WITH SAID TRANSVERSE MEDIAL FACES, RESPECTIVELY. 